EP0354342B1 - Machine de déplacement de fluide de type à spirale - Google Patents

Machine de déplacement de fluide de type à spirale Download PDF

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Publication number
EP0354342B1
EP0354342B1 EP89112051A EP89112051A EP0354342B1 EP 0354342 B1 EP0354342 B1 EP 0354342B1 EP 89112051 A EP89112051 A EP 89112051A EP 89112051 A EP89112051 A EP 89112051A EP 0354342 B1 EP0354342 B1 EP 0354342B1
Authority
EP
European Patent Office
Prior art keywords
bearing
housing
rotor
guide
guide shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89112051A
Other languages
German (de)
English (en)
Other versions
EP0354342A1 (fr
Inventor
Gregor Jetzer
Roland Kolb
Fritz Spinnler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
Aginfor AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CH293988A external-priority patent/CH675451A5/de
Application filed by Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0354342A1 publication Critical patent/EP0354342A1/fr
Application granted granted Critical
Publication of EP0354342B1 publication Critical patent/EP0354342B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F01C1/0223—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements

Definitions

  • the invention relates to a displacement machine for compressible media with at least one conveying space arranged in a fixed housing, designed in the manner of a spiral slot, and with an equally spiral displacing body assigned to each conveying space, which is held in this way on a disk-shaped rotor which can be driven eccentrically with respect to the housing that during operation each of its points executes a circular movement delimited by the circumferential walls of the displacement chamber, and its curvature relative to that of the delivery chamber is dimensioned such that it almost touches the inner and outer circumferential walls of the delivery chamber on at least one sealing line continuously progressing during operation, wherein for guiding the rotor relative to the housing relative to a first eccentric arrangement, a second eccentric arrangement is provided, the second of which is arranged in the housing mounted guide shaft is positively connected to the drive shaft of the first eccentric arrangement via a gear.
  • Displacement machines of the spiral type are known for example from DE-C-26 03 462.
  • a compressor constructed according to this principle is characterized by an almost pulsation-free conveyance of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and could therefore also be used with advantage for charging purposes of internal combustion engines, among other things.
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • the two peripheral walls of the displacement chamber which move from the inlet through the displacement chamber to the outlet, their volume constantly decreasing and the pressure of the work equipment is increased accordingly.
  • a machine of the type mentioned at the outset is known from DE-A-3 313 000.
  • a guide shaft of the second eccentric arrangement mounted in the housing is positively connected to the drive shaft via a gear, the gear being formed, for example, by a toothed belt drive.
  • a precise rolling of a displacer according to the spiral principle by a translatory circular movement is achieved by a double crank drive, as is known for example from DE-A-3 230 979 and in which one crank drives and the second crank guides.
  • this known solution provides a length-adjustable transmission element, in the direction of the connecting line of the points of attack.
  • This transmission member consists of a holding member which is adjustably held in the guide arrangement of the rotor, which can be a sliding block which can be displaced in a parallel guide.
  • the parallel guide comprises one of the two bearings of the guide arrangement, via which a possible compensation of expansion differences can take place.
  • a bearing arrangement provided with an elastic bedding is provided on at least one of the points of attack, preferably at the point of application of the guide device .
  • This elastic bedding can be formed, for example, by a rubber-elastic ring which sits between the bearing outer ring and the bearing eye.
  • both shafts are mounted in roller bearings.
  • the drive shaft in the housing is mounted in two ball bearings and the eccentric collar arranged on the drive shaft is supported by a roller bearing
  • the guide shaft in the housing is supported by two ball bearings and the eccentric pin the guide shaft is supported in the rotor disk via a needle bearing.
  • the needle bearing in the rotor disk is usually grease-lubricated (DE-A-3 638 470), while the highly loaded eccentric bearing of the drive shaft is oil-lubricated (DE-A-3 320 086).
  • the object of the invention is to simplify the bearing concept of the displacement machine with regard to cost optimization and, in particular, to take a measure , with which the previous means for resilient inclusion of any length differences can be dispensed with.
  • the guide shaft is hollow and communicates with the lubricant outlet of the slide bearing via a wall bore, and if the hollow interior is connected to the lubrication chamber of the guide bearing via a longitudinal bore in the eccentric bolt of the guide shaft.
  • FIGS. 1 and 2 For the sake of clarity, the machine is shown in FIGS. 1 and 2 in the disassembled state.
  • the rotor of the machine is designated as a whole by 1.
  • two spiral-shaped displacers are arranged, which are offset by 180 ° to one another. It is strips 3.3 ', which are held vertically on the disc 2.
  • the spirals themselves are formed from a plurality of circular arcs connected to one another. 4 with the hub is designated with which the disc 2 is mounted on a roller bearing 22. The bearing itself sits on an eccentric disk 23, which in turn is part of the drive shaft 24. 5 with a radially outside of the strips 3,3 'arranged eye is designated for receiving a guide bearing 25 which is mounted on an eccentric bolt 26. This is in turn part of a guide shaft 27.
  • two openings 6 are provided in the disk so that the medium can get from one disk side to the other, for example to be drawn off in a central outlet arranged only on one side.
  • Fig. 1 the housing half 7 shown in Fig. 3 left of the two halves 7,7 'assembled, via fastening eyes 8 for receiving screw connections interconnected machine housing is shown.
  • 9 symbolizes the holder for the drive shaft, 10 the holder for the guide shaft.
  • 11 and 11 ' denote the two delivery spaces, each offset by 180 °, which are incorporated in the manner of a spiral slot in the two housing halves. They each run from an inlet 12, 12 'arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24, respectively. 26.27.
  • the drive shaft 24 is mounted in the roller bearings 17 and 18 and provided at its end protruding from the housing half 7 with a V-belt pulley 19 for the drive.
  • Counterweights 20 are arranged on the drive shaft 24 to compensate for the inertial forces arising when the rotor is eccentrically driven.
  • Such a balancing mass 21 is also attached to the guide shaft 27.
  • This guide shaft is inserted within the housing half 7 in a slide bearing 28 which is sealed on both sides with ring seals 39.
  • the two eccentric arrangements are synchronized with a precise angle via a toothed belt drive 16.
  • This double eccentric drive ensures that all points of the rotor disc and thus all points of the two strips 3 and 3 'perform a circular displacement movement.
  • crescent-shaped work spaces enclosing the working medium result on both sides of the strips, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet .
  • the volumes of these working spaces decrease and the pressure of the working fluid is increased accordingly.
  • Lubricant preferably oil
  • a lubricant source not shown
  • the oil is collected on both sides of this bearing and guided through a bore 30 into the area of the drive shaft 24. There, part of the oil is used to lubricate the rolling bearing 17.
  • longitudinal bores 31 ', 31 ⁇ are provided, which are processed together for manufacturing reasons and are subsequently divided by a plug 32 attached in the plane of the roller bearing 22.
  • the lubricating oil is introduced into the longitudinal bore 31 '.
  • the eccentric disc 23 branch from the longitudinal bores 31 ', 31 ⁇ radially directed transverse bores 34 and 35.
  • the longitudinal bore 31 ⁇ opens into a chamber 37, from which, on the one hand, the roller bearing 18 is acted upon and from which the lubricant is guided out of the other via a bore 38 from the housing half 7 '.
  • Fig. 3 shows an embodiment of the guide shaft 27 'during operation, that is with circulating lubricant.
  • This solution also makes it possible to use the lubricant to lubricate the guide bearing 25.
  • the well 27 ' is hollow.
  • the drive-side end of the hollow interior 42 is provided with a cover 44.
  • the shaft 27 ' is penetrated with a wall bore 41 which is arranged in the plane of the lubricant outlet 40.
  • this wall hole could also be in the plane of the drive-side lubricant outlet 40 '.
  • the lubricant outlets 40, 40 ' provided on both sides of the slide bearing are connected to one another via the bore 46.
  • the eccentric bolt 26 ' has a longitudinal bore 43 which penetrates the bolt over its entire length and opens into the lubricating space of the guide bearing 25.
  • a lubricant ring 46 forms on the walls in the hollow interior. This ring supplies the guide bearing 25 with lubricant via the bore 43.
  • an overpressure arises in the communicating system. This is so large that the lubricant reaches the hollow interior 42 via the wall bore 41 and forms the lubricant ring 46 there.
  • This ring has a strength of Rs, where R is the outer radius of the guide shaft 27 'and s is the distance from the shaft axis to the inner wall of the lubricant ring.
  • the overpressure in the communicating lubricant system depends on the speed.
  • the strength of the lubricant ring depends on the length of the bore 30 and the outer radius of the guide shaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Transmission Devices (AREA)

Claims (2)

  1. Machine volumétrique pour milieux compressibles avec au moins une chambre d'alimentation (11, 11') disposée dans un logement fixe (7, 7'), configurée à la manière d'une fente s'étendant en forme de spirale, et avec un corps volumétrique (1-4) également configuré en forme de spirale, associé à chaque chambre d'alimentation, maintenu de telle sorte sur un rotor (1) en forme de disque entraînable de manière excentrique par rapport au logement, que lors du fonctionnement, chacun de ses points décrive un mouvement circulaire limité par les parois périphériques de la chambre d'alimentation, et dont la courbure par rapport à celle de la chambre d'alimentation est dimensionnée de telle manière qu'il entre presque en contact avec les parois interne et externe de la chambre d'alimentation suivant chaque fois au moins une ligne d'étanchéité progressant de manière continue lors du fonctionnement, un deuxième dispositif à excentrique (26, 26', 27, 27') disposé à une certaine distance d'un premier dispositif à excentrique (23, 24) étant prévu pour le guidage du rotor par rapport au logement et dont l'arbre de guidage (27, 27') placé dans le logement est raccordé rigidement à l'arbre menant (24) du premier dispositif à excentrique par l'intermédiaire d'un engrenage (16),
    caractérisée en ce que
    l'arbre de guidage (27, 27') et l'arbre menant (24) sont placés dans le logement (7) au moyen d'un palier à glissement (28) et au moyen d'un palier à roulement (17) respectivement,
    en ce que le palier à glissement (28) et le palier à roulement (17) sont graissés à l'huile, l'huile se rassemblant dans la sortie d'huile (40, 40') du palier à glissement après avoir réalisé sa fonction de graissage dans celui-ci (28) étant acheminée par une conduite (30) pour alimenter le palier à roulement (17) en huile,
    et en ce que le palier guide (25) pour le boulon d'excentrique (26, 26') de l'arbre menant (27, 27') est alimenté avec l'huile rassemblée à la sortie d'huile (40, 40') du palier à glissement (28).
  2. Machine volumétrique selon la revendication 1, caractérisée en ce que l'arbre menant (27') a une configuration creuse et communique avec la sortie d'huile (40) du palier à glissement par l'intermédiaire d'un trou (41) dans la paroi, et en ce que l'espace interne creux (42) est en communication avec l'espace de graissage du palier guide (25) par l'intermédiaire d'un trou longitudinal (43) dans le boulon d'excentrique (26') de l'arbre menant.
EP89112051A 1988-08-03 1989-07-01 Machine de déplacement de fluide de type à spirale Expired - Lifetime EP0354342B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH293988A CH675451A5 (en) 1988-08-03 1988-08-03 Displacement machine with spiral displacement member
CH2939/88 1988-08-03
CH215089 1989-06-08
CH2150/89 1989-06-08

Publications (2)

Publication Number Publication Date
EP0354342A1 EP0354342A1 (fr) 1990-02-14
EP0354342B1 true EP0354342B1 (fr) 1994-01-05

Family

ID=25689652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89112051A Expired - Lifetime EP0354342B1 (fr) 1988-08-03 1989-07-01 Machine de déplacement de fluide de type à spirale

Country Status (6)

Country Link
US (1) US5024589A (fr)
EP (1) EP0354342B1 (fr)
JP (1) JPH0481588A (fr)
KR (1) KR900003539A (fr)
BR (1) BR8903891A (fr)
DE (1) DE58906623D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102865245A (zh) * 2012-10-19 2013-01-09 溧阳市超强链条制造有限公司 给吊扇轴承加润滑油的结构及其加油方法

Families Citing this family (35)

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Publication number Priority date Publication date Assignee Title
DE69132650T2 (de) * 1990-02-13 2002-05-08 Anest Iwata Corp Spiralverdrängungsmaschine
EP0545187B1 (fr) * 1991-12-05 1996-01-24 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale
EP0545191B1 (fr) * 1991-12-05 1995-09-13 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale
EP0547470B1 (fr) * 1991-12-16 1995-08-23 AGINFOR AG für industrielle Forschung Machine à déplacement positif selon le principle de la spirale
DE4208312A1 (de) * 1992-03-16 1993-09-23 Asea Brown Boveri Verdraengermaschine nach dem spiralprinzip
EP0614012B1 (fr) * 1993-01-19 1996-09-18 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide du type à spirales
DE59400711D1 (de) * 1993-03-17 1996-10-31 Aginfor Ag Brennkraftmaschine mit Lader nach dem Verdrängerprinzip
DE19528071A1 (de) * 1995-07-31 1997-02-06 Knorr Bremse Systeme Spiralverdichter
JP3423514B2 (ja) * 1995-11-30 2003-07-07 アネスト岩田株式会社 スクロール流体機械
JP3985051B2 (ja) * 1997-07-28 2007-10-03 独立行政法人 日本原子力研究開発機構 ダブルラップドライスクロール真空ポンプ
ES2164398T3 (es) * 1997-08-26 2002-02-16 Crt Common Rail Tech Ag Maquinas de desplazamiento espiral para medios compresibles.
JPH1182333A (ja) * 1997-09-12 1999-03-26 Kimie Nakamura スクロール流体機械
JP2001516848A (ja) * 1997-09-16 2001-10-02 アテリエ ビスク ソシエテ アノニム らせん式真空ポンプ
US7371059B2 (en) * 2006-09-15 2008-05-13 Emerson Climate Technologies, Inc. Scroll compressor with discharge valve
EP2137412B1 (fr) * 2007-04-17 2012-12-05 Spinnler Engineering Machine de refoulement construite selon le principe de la spirale
ATE533920T1 (de) * 2007-08-22 2011-12-15 Spinnler Engineering Verdrängermaschine nach dem spiralprinzip
DE102007043594B4 (de) * 2007-09-13 2009-11-26 Handtmann Systemtechnik Gmbh & Co. Kg Spiralverdichter mit Doppelspirale
US7988433B2 (en) 2009-04-07 2011-08-02 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
JP5280315B2 (ja) 2009-08-18 2013-09-04 本田技研工業株式会社 内燃機関の過給機潤滑構造
DE102011103165A1 (de) * 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Ladevorrichtung zur Verdichtung von Ladeluft für einen Verbrennungsmotor
JP5931564B2 (ja) * 2012-04-25 2016-06-08 アネスト岩田株式会社 両回転型スクロール膨張機及び該膨張機を備えた発電装置
US9651043B2 (en) 2012-11-15 2017-05-16 Emerson Climate Technologies, Inc. Compressor valve system and assembly
US9249802B2 (en) 2012-11-15 2016-02-02 Emerson Climate Technologies, Inc. Compressor
JP6345081B2 (ja) * 2014-10-31 2018-06-20 アネスト岩田株式会社 スクロール膨張機
JP6441645B2 (ja) * 2014-11-07 2018-12-19 アネスト岩田株式会社 スクロール流体機械
US9790940B2 (en) 2015-03-19 2017-10-17 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10598180B2 (en) 2015-07-01 2020-03-24 Emerson Climate Technologies, Inc. Compressor with thermally-responsive injector
US10890186B2 (en) 2016-09-08 2021-01-12 Emerson Climate Technologies, Inc. Compressor
US10801495B2 (en) 2016-09-08 2020-10-13 Emerson Climate Technologies, Inc. Oil flow through the bearings of a scroll compressor
US10753352B2 (en) 2017-02-07 2020-08-25 Emerson Climate Technologies, Inc. Compressor discharge valve assembly
US11022119B2 (en) 2017-10-03 2021-06-01 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10962008B2 (en) 2017-12-15 2021-03-30 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10995753B2 (en) 2018-05-17 2021-05-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US11655813B2 (en) 2021-07-29 2023-05-23 Emerson Climate Technologies, Inc. Compressor modulation system with multi-way valve
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102865245A (zh) * 2012-10-19 2013-01-09 溧阳市超强链条制造有限公司 给吊扇轴承加润滑油的结构及其加油方法
CN102865245B (zh) * 2012-10-19 2015-04-08 溧阳市超强链条制造有限公司 给吊扇轴承加润滑油的结构及其加油方法

Also Published As

Publication number Publication date
KR900003539A (ko) 1990-03-26
US5024589A (en) 1991-06-18
JPH0481588A (ja) 1992-03-16
DE58906623D1 (de) 1994-02-17
BR8903891A (pt) 1990-03-27
EP0354342A1 (fr) 1990-02-14

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